WO2014027640A1 - 渦電流式減速装置 - Google Patents

渦電流式減速装置 Download PDF

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Publication number
WO2014027640A1
WO2014027640A1 PCT/JP2013/071799 JP2013071799W WO2014027640A1 WO 2014027640 A1 WO2014027640 A1 WO 2014027640A1 JP 2013071799 W JP2013071799 W JP 2013071799W WO 2014027640 A1 WO2014027640 A1 WO 2014027640A1
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WO
WIPO (PCT)
Prior art keywords
eddy current
braking
disk
magnet holding
brake
Prior art date
Application number
PCT/JP2013/071799
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
山口　博行
今西　憲治
野口　泰隆
敬士 二葉
Original Assignee
新日鐵住金株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 新日鐵住金株式会社 filed Critical 新日鐵住金株式会社
Priority to US14/408,671 priority Critical patent/US9933032B2/en
Priority to KR1020157000955A priority patent/KR101671127B1/ko
Priority to IN412DEN2015 priority patent/IN2015DN00412A/en
Priority to JP2014530551A priority patent/JP5673899B2/ja
Priority to CN201380038230.0A priority patent/CN104488177B/zh
Priority to EP13879586.9A priority patent/EP2884640B1/en
Publication of WO2014027640A1 publication Critical patent/WO2014027640A1/ja

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L7/00—Electrodynamic brake systems for vehicles in general
    • B60L7/02—Dynamic electric resistor braking
    • B60L7/06—Dynamic electric resistor braking for vehicles propelled by ac motors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L7/00—Electrodynamic brake systems for vehicles in general
    • B60L7/28—Eddy-current braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
    • F16D63/002—Brakes with direct electrical or electro-magnetic actuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/78—Features relating to cooling
    • F16D65/84—Features relating to cooling for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/78—Features relating to cooling
    • F16D65/84—Features relating to cooling for disc brakes
    • F16D65/853—Features relating to cooling for disc brakes with closed cooling system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
    • H02K49/02—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type
    • H02K49/04—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type
    • H02K49/043—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type with a radial airgap
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
    • H02K49/02—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type
    • H02K49/04—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type
    • H02K49/046—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type with an axial airgap
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
    • H02K49/10—Dynamo-electric clutches; Dynamo-electric brakes of the permanent-magnet type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2200/00—Type of vehicles
    • B60L2200/18—Buses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2200/00—Type of vehicles
    • B60L2200/40—Working vehicles
    • B60L2200/44—Industrial trucks or floor conveyors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/001—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P90/00—Enabling technologies with a potential contribution to greenhouse gas [GHG] emissions mitigation
    • Y02P90/60—Electric or hybrid propulsion means for production processes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility

Definitions

  • the present invention relates to an eddy current type reduction gear mounted as an auxiliary brake on a transportation means such as a vehicle such as a truck or a bus, and more particularly to an eddy current type reduction gear using a permanent magnet for generating a braking force.
  • an eddy current type speed reducer (hereinafter also simply referred to as “speed reducer”) using a permanent magnet (hereinafter also simply referred to as “magnet”) has a braking member fixed to a rotating shaft such as a propeller shaft, During braking, an eddy current is generated on the surface of the braking member facing the magnet by the action of the magnetic field from the magnet, and this eddy current causes a braking force in the direction opposite to the rotation direction to the braking member that rotates integrally with the rotating shaft. Is generated, and the rotational axis is decelerated.
  • the speed reducer is roughly divided into a drum type and a disk type according to the shape of a braking member that generates a braking force by generating an eddy current, and a magnet holding member that holds the magnet and forms a pair with the braking member.
  • a braking member that generates a braking force by generating an eddy current
  • a magnet holding member that holds the magnet and forms a pair with the braking member.
  • FIG. 1 is a longitudinal sectional view showing a configuration example of a conventional synchronous rotation speed reduction device.
  • the speed reduction device shown in FIG. 1 is a disk type, and includes a braking disk 101 as a braking member and a magnet holding disk 104 that holds a permanent magnet 105 facing the main surface of the braking disk 101 as a magnet holding member.
  • the brake disc 101 is configured to rotate integrally with a rotating shaft 111 such as a propeller shaft.
  • the connecting shaft 112 is fixed on the same axis as the rotating shaft 111 with a bolt or the like, and a sleeve 113 with a flange is inserted into the connecting shaft 112 while being engaged with the spline 112 and fixed with a nut 114.
  • the brake disc 101 is fixed to the flange of the sleeve 113 integrated with the rotating shaft 111 with a bolt or the like, and thereby rotates integrally with the rotating shaft 111.
  • the brake disc 101 is provided with, for example, heat radiation fins 102 on the outer periphery thereof.
  • the heat dissipating fins 102 are integrally formed with the brake disc 101 and serve to cool the brake disc 101 itself.
  • the material of the brake disk 101 is a conductive material, among which a ferromagnetic material such as iron, a weak magnetic material such as ferritic stainless steel, or a nonmagnetic material such as an aluminum alloy or a copper alloy may be used.
  • the magnet holding disk 104 is configured to be rotatable with respect to the rotating shaft 111.
  • the magnet holding disk 104 may be integrally formed with the annular member 103 concentric with the connecting shaft 112, or may be individually formed and fixed to the annular member 103 with a bolt or the like.
  • the annular member 103 is supported by a sleeve 113 integrated with the rotating shaft 111 via bearings 115 a and 115 b, so that the magnet holding disk 104 can rotate relative to the rotating shaft 111.
  • the bearings 115 a and 115 b are filled with lubricating grease, and the lubricating grease is prevented from leaking by ring-shaped seal members 116 a and 116 b attached to both front and rear ends of the annular member 103.
  • a plurality of permanent magnets 105 are fixed to the surface of the magnet holding disk 104 facing the main surface of the brake disk 101 in the circumferential direction.
  • the permanent magnets 105 are arranged such that the magnetic poles (N pole, S pole) are oriented in the axial direction of the magnet holding disk 104 and the magnetic poles are alternately different between those adjacent in the circumferential direction.
  • a magnet cover 120 made of a thin plate is attached to the magnet holding disk 104 so as to cover the entire permanent magnet 105.
  • the magnet cover 120 protects the permanent magnet 105 from iron powder and dust, and suppresses the radiant heat from the braking disk 101 to the permanent magnet 105 in order to prevent the magnetic force possessed by the permanent magnet 105 from being reduced by the heat effect. Play the role of blocking.
  • the material of the magnet cover 120 is a nonmagnetic material so as not to affect the magnetic field from the permanent magnet 105.
  • the disc brake includes a disk brake as a friction brake for stopping the magnet holding disk 104 during braking.
  • the disc brake includes a brake disc 106 disposed behind the magnet holding disc 104 and integral with the annular member 103, a brake caliper 107 having brake pads 108a and 108b sandwiching the brake disc 106, and the brake An electric linear actuator 109 that drives the caliper 107 is included.
  • the brake disk 106 is attached to the annular member 103 with a bolt or the like, and is integrated with the annular member 103.
  • the brake caliper 107 has a pair of brake pads 108a and 108b at the front and rear, and the brake disc 106 is disposed oppositely with a predetermined gap between the brake pads 108a and 108b, and a bracket is mounted by a bolt or the like mounted with a spring. It is biased and supported toward 117.
  • the bracket 117 is attached to a non-rotating portion such as a vehicle chassis or a cross member.
  • the bracket 117 surrounds the annular member 103 at a position rearward of the brake disk 106 and is rotatably supported by the annular member 103 via a bearing 118.
  • the bearing 118 is also filled with lubricating grease, and leakage of the lubricating grease is prevented by ring-shaped seal members 119a and 119b attached to the front and rear ends of the bracket 117.
  • the actuator 109 is fixed to the brake caliper 107 with a bolt or the like.
  • the actuator 109 is driven by the electric motor 110, converts the rotational motion of the electric motor 110 into a linear motion, and moves the rear brake pad 108 b linearly toward the brake disk 106.
  • the rear brake pad 108b presses the brake disc 106, and the action of the reaction force associated therewith moves the front brake pad 108a toward the brake disc 106.
  • the brake disc 106 is moved back and forth.
  • the brake pads 108a and 108b are firmly inserted.
  • the disc brake (friction brake) is not operated when not braking.
  • the brake disk 101 is a ferromagnetic material or a weak magnetic material
  • the magnet holding disk 104 integrated with the annular member 103 is replaced with the permanent magnet 105 as the brake disk 101 rotates together with the rotating shaft 111. Due to the magnetic attraction with the brake disk 101, it rotates in synchronization with the brake disk 101. For this reason, since a relative rotational speed difference does not occur between the brake disk 101 and the permanent magnet 105, no braking force is generated.
  • the brake disk 101 When the brake disk 101 is a non-magnetic material, no magnetic attractive force acts between the magnet 105 and the brake disk 101, but as the brake disk 101 rotates in the magnetic field exerted by the magnet 105, the brake disk 101 A braking force is generated in 101 by the action of a magnetic field. Therefore, the magnet 105 receives the reaction force and rotates in the same direction as the brake disk 101. That is, the braking force generated by the relative rotational speed difference between the braking disk 101 and the magnet 105 is balanced with the drag of the air resistance caused by the rotation of the magnet holding disk 104 and the loss of the bearing caused by the rotation of the magnet 105. The magnet 105 rotates in the same direction as the brake disk 101 while generating a slight relative rotational speed difference. That is, when the brake disk 101 is a non-magnetic material, the magnet 105 does not rotate completely synchronously with the brake disk 101, but rotates with the slight rotation speed difference and substantially synchronously. The non-braking state is maintained.
  • the disc brake (friction brake) is operated, and the brake disc 106 is sandwiched between the brake pads 108a and 108b, whereby the rotation of the magnet holding disc 104 integral with the annular member 103 is stopped, and the magnet holding disc 104 stops. If only the magnet holding disk 104 is stationary while the brake disk 101 is rotating, a relative rotational speed difference is generated between the brake disk 101 and the permanent magnet 105. Therefore, an eddy current is generated on the main surface of the brake disk 101 by the action of the magnetic field from the permanent magnet 105, and a braking force can be generated on the rotating shaft 111 via the brake disk 101.
  • the braking state is the same in principle due to the action of a magnetic field, regardless of whether the brake disk 101 is made of a ferromagnetic material or a non-magnetic material. Because of the difference in efficiency, the material of the brake disk 101 can be selected as appropriate when designing the magnetic circuit.
  • the speed reduction device shown in FIG. 1 has a configuration in which the braking disk 101 as a braking member is connected to the rotating shaft 111 and the magnet holding disk 104 as a magnet holding member is rotatably supported on the rotating shaft 111.
  • a configuration in which the brake disk 101 and the magnet holding disk 104 are replaced with each other is also realized. That is, the object fixed to the rotating shaft 111 may be the magnet holding disk 104, and the object supported rotatably on the rotating shaft 111 may be the braking disk 101.
  • the rotation of the annular member 103 is stopped by the operation of the disc brake, and the braking disc 101 is stopped. If only the brake disk 101 is stationary while the magnet holding disk 104 is rotating, a relative rotational speed difference is generated between the brake disk 101 and the permanent magnet 105 in the magnet holding disk 104. Therefore, an eddy current is generated on the main surface of the brake disk 101. As a result, due to the interaction between the eddy current generated on the main surface of the braking disk 101 and the magnetic flux density from the permanent magnet 105, the rotating magnet holding disk 104 has a braking force in the direction opposite to the rotational direction in accordance with Fleming's left-hand rule. The rotation of the rotating shaft 111 can be decelerated through the magnet holding disk 104.
  • Japanese Laid-Open Patent Publication No. 4-331456 Japanese National Utility Model Publication No. 5-80178 Japanese Unexamined Patent Publication No. 2011-97696 Japanese Unexamined Patent Publication No. 2011-139574 Japanese Unexamined Patent Publication No. 2011-182574
  • the conventional synchronous rotation type reduction gear described above has the following problems.
  • a friction brake (disc brake) is indispensable in order to stop a member that is rotatably supported on the rotating shaft among the braking member and the magnet holding member at the time of braking, and the braking member and the brake disc are connected in series. If it connects to, the dimension of the speed reducer in an axial direction will become large.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a synchronous rotation type eddy current reduction device that is reduced in size by reducing the axial dimension of the device.
  • An eddy current reduction device includes a magnet holding member that is provided coaxially with a rotating shaft and holds a plurality of permanent magnets in a circumferential direction; A pair of disk portions disposed on both sides in the axial direction of the rotating shaft; a connecting portion that connects the pair of disk portions; and an eddy current generating portion that generates an eddy current by the rotation of the permanent magnet. And a braking member that is rotatably supported relative to the rotation shaft; and a friction brake that presses the friction member against the braking member during braking and stops the braking member.
  • the braking member may cover the periphery of the magnet holding member.
  • the plurality of permanent magnets are configured such that different magnetic poles are alternately arranged in a circumferential direction on a surface orthogonal to the rotation axis of the magnet holding member. You may employ
  • the plurality of permanent magnets are disposed in through holes formed in the circumferential direction of the magnet holding member so as to penetrate the magnet holding member in the axial direction of the rotating shaft.
  • a configuration may be adopted in which the respective poles are arranged so as to face the eddy current generating portions formed on the inner surfaces of both of the pair of disk portions.
  • the connecting portion is a cylindrical member that connects the pair of disk portions on the outer periphery and has the eddy current generating portion formed on the inner peripheral surface thereof.
  • the plurality of permanent magnets are arranged in the radial direction of the magnet holding member so that different magnetic poles are alternately arranged in the circumferential direction on the outer peripheral side of the magnet holding member, and are opposed to the eddy current generating unit. A configuration may be adopted.
  • the connecting part is a cylindrical part that connects the pair of disk parts at the outer periphery, and at least one inner surface of the pair of disk parts and the The eddy current generating portion is formed on the inner peripheral surface of the cylindrical portion; the plurality of permanent magnets are arranged on the outer periphery of the magnet holding member so that magnetic poles are alternately arranged in the circumferential direction; and the plurality of permanent magnets Ferromagnetic materials are interposed therebetween, and these ferromagnetic materials are opposed to the eddy current generator; a configuration may be adopted.
  • an impeller connected to the rotating shaft may be further provided adjacent to each outer surface of the pair of disk portions.
  • the friction brake is fixed to a non-rotating portion of a vehicle including the rotating shaft, and the pair of disk portions are used as the friction members.
  • a brake caliper including a pair of sandwiched brake pads; and an actuator that drives the brake caliper and moves the pair of brake pads toward the disc portion.
  • a temperature sensor that contacts the outer surface of the disc portion in conjunction with the movement of the brake pad toward the disc portion and detects the temperature of the disc portion; And an actuator controller that releases driving of the actuator when the temperature of the disk portion detected by the temperature sensor exceeds a predetermined temperature.
  • a cooling member that contacts the outer surface of the disc portion in conjunction with the movement of the brake pad toward the disc portion may be further provided.
  • a plurality of winding coils may be embedded along the circumferential direction in a region where the braking member faces the permanent magnet.
  • the axial dimension can be reduced and the size can be reduced. Further, when the magnet holding member is surrounded by the braking member as in the above-described aspect (2), foreign matter can be prevented from entering the gap between the braking member and the permanent magnet, and consequently the braking member and the permanent magnet can be prevented from entering. It can suppress that a foreign material adheres to a clearance gap.
  • FIG. 3A It is a schematic diagram which shows the whole structure of the synchronous-rotation type
  • FIG. 5A It is a figure which shows schematic structure of the modification of the synchronous-rotation type
  • FIG. 5A It is a figure which shows schematic structure of the synchronous-rotation type
  • the present inventors have rotated the magnet holding member in order to reduce the axial dimension of the device in the synchronous rotation type reduction device using a permanent magnet.
  • a braking member is disposed so as to be connected to a shaft so as to sandwich the magnet holding member in the axial direction of the rotating shaft, and the braking member is rotatably supported on the rotating shaft, and a friction member is attached to the braking member during braking.
  • the present invention has been completed with the knowledge that it is effective to construct a friction brake that presses against and stops the braking member.
  • the magnet holding member is fixed to the rotating shaft, and the braking member is configured so as to surround the entire magnet holding member.
  • the present invention has obtained the knowledge that it is effective to employ a friction brake that rotatably supports a braking member on a rotating shaft and then presses the friction member against the braking member during braking to make the braking member stationary. Was completed.
  • FIG. 2A is a schematic diagram showing the overall configuration of the synchronous rotation speed reduction device according to the first embodiment of the present invention, and shows a side view partly in section.
  • FIG. 2B shows a cross-sectional view taken along the line IIB-IIB of FIG. 2A.
  • FIG. 2C is a diagram showing a IIC-IIC cross section of FIG. 2B.
  • the synchronous rotation speed reduction device corresponds to a disk type, and includes a magnet holding member 4 that holds a permanent magnet 5 and a braking member 1, and the braking member 1 is a magnet holding member. It is set as the structure which surrounds the whole of 4 from the outside.
  • the magnet holding member 4 has a disk shape in which surfaces orthogonal to the rotation shaft 11 are formed on both sides in the axial direction of the rotation shaft 11, and is connected to the rotation shaft 11 and integrated with the rotation shaft 11. Is configured to rotate.
  • the tubular connecting shaft 12 is fixed to the rotating shaft 11 coaxially by a bolt or the like, and the magnet holding member 4 is fixed to the connecting shaft 12 via a sleeve 13 press-fitted into the connecting shaft 12. Yes. Thereby, the magnet holding member 4 comes to rotate integrally with the rotating shaft 11.
  • the magnet holding member 4 is formed with windows (through holes) penetrating in the axial direction at equal angular intervals in the circumferential direction, and the permanent magnet 5 is formed in each of the windows. It shows a mode in which they are inserted one by one and fixed using an adhesive or a metal fitting. As a result, the permanent magnet 5 is exposed on both surfaces in the axial direction of the rotating shaft 11 of the magnet holding member 4 and is opposed to both inner surfaces of the pair of disk portions 1a and 1b (described later).
  • Each permanent magnet 5 is arranged such that the direction of the magnetic pole (N pole, S pole) is parallel to the axial direction of the rotating shaft 11, that is, the axial direction of the magnet holding member 4. Further, the permanent magnets 5 are arranged such that the magnetic poles are alternately changed in the circumferential direction when viewed on a plane orthogonal to the rotation shaft 11 of the magnet holding member 4.
  • the material of the magnet holding member 4 is a non-magnetic material such as aluminum or austenitic stainless steel at least around the window around the permanent magnet 5 in the case where the permanent magnet 5 is inserted into a window penetrating in the axial direction. It is desirable.
  • the portion connected to the rotating shaft 11 may be a non-magnetic material or a ferromagnetic material such as carbon steel.
  • the braking member 1 includes a pair of donut-shaped disk parts 1 a and 1 b and a cylindrical part (connecting part) 1 c that connects these disk parts 1 a and 1 b on the outer periphery, and surrounds the magnet holding member 4. However, it is configured to be rotatable with respect to the rotating shaft 11.
  • the inner surfaces of the disk portions 1 a and 1 b are opposed to both surfaces of the magnet holding member 4, and the inner peripheral surface of the cylindrical portion 1 c is opposed to the outer peripheral surface of the magnet holding member 4.
  • the inner surfaces of the pair of disk portions 1a and 1b constitute an eddy current generating portion.
  • Each disk part 1a, 1b is supported by a sleeve 13 integrated with the rotary shaft 11 via bearings 15a, 15b, whereby the braking member 1 has a pair of disk parts 1a, 1b and a cylindrical part 1c. Integrally, it can rotate freely with respect to the rotating shaft 11.
  • the front disk part 1a and the cylindrical part 1c are integrally molded, and the rear disk part 1b is integrated with a bolt or the like.
  • the material of the disk parts 1 a and 1 b is a conductive material, among which carbon steel, cast iron, etc. Ferromagnetic materials, weak magnetic materials such as ferritic stainless steel, or nonmagnetic materials such as aluminum alloys and copper alloys are preferred.
  • the surface layer portion of the inner surface facing the permanent magnet 5 in the disk portions 1a and 1b is a highly conductive material such as copper or a copper alloy. It is more preferable that
  • the braking member 1 is provided with a plurality of heat radiation fins 2 integrally formed with the cylindrical portion 1c on the outer periphery thereof.
  • the heat radiating fins 2 may be provided in a region where there is no hindrance to the arrangement of the friction member of the friction brake described later, for example, in the region of the inner peripheral portion of the outer surface.
  • the heat radiating fins 2 serve to cool the braking member 1 itself.
  • the 2A includes a friction brake that stops the braking member 1 during braking.
  • the friction brake includes a brake caliper 7 having brake pads 8a and 8b as friction members that sandwich the outer peripheral portion of the braking member 1, that is, the outer peripheral portions of the outer surfaces of the disc portions 1a and 1b, from both sides in the axial direction.
  • An electric linear actuator 9 that drives the caliper 7 is included.
  • the brake caliper 7 has a pair of brake pads 8a and 8b at the front and rear, and a spring is mounted in a state where the braking member 1 is disposed between the brake pads 8a and 8b with a predetermined gap therebetween. It is urged and supported toward the bracket 17 by a bolt or the like.
  • the bracket 17 is attached to a non-rotating part of the vehicle.
  • the bracket 17 is rotatably supported by a sleeve 13 integrated with the rotary shaft 11 via a bearing 18.
  • the bracket 17 does not need to be supported via the bearing 18 if it is fixed to the transmission cover (non-rotating portion). This is because the transmission cover is supported via a bearing.
  • the actuator 9 is fixed to the brake caliper 7 with a bolt or the like.
  • the actuator 9 is driven by, for example, the electric motor 10, converts the rotational motion of the electric motor 10 into a linear motion, and linearly moves the rear brake pad 8b toward the rear disc portion 1b.
  • the rear brake pad 8b presses the rear disc portion 1b
  • the front brake pad 8a moves toward the front disc portion 1a by the action of the reaction force associated therewith.
  • the braking member 1 is strongly sandwiched between the front and rear brake pads 8a and 8b.
  • the friction brake is not operated when not braked.
  • the pair of disk portions 1 a and 1 b constituting the braking member 1 are magnetically attracted by the permanent magnet 5 held by the magnet holding member 4 (braking member).
  • 1 is a magnetic material) or is rotated in synchronization with the magnet holding member 4 by the action of a magnetic field (when the braking member 1 is a non-magnetic material). For this reason, since a relative rotational speed difference does not arise between the disk parts 1a and 1b (braking member 1) and the permanent magnet 5 in the magnet holding member 4, no braking force is generated.
  • the friction brake when the friction brake is operated during braking, the braking member 1 is sandwiched between the brake pads 8a and 8b, which are friction members, whereby the rotation of the braking member 1 is stopped and the braking member 1 is stopped.
  • the braking member 1 When the braking member 1 is stationary while the magnet holding member 4 is rotating, there is a relative rotational speed difference between the disk portions 1 a and 1 b (braking member 1) and the permanent magnet 5 in the magnet holding member 4. Arise. Therefore, eddy currents are generated on the inner surfaces of the disk portions 1a and 1b.
  • a separate and independent brake disk 106 required in the conventional reduction gear shown in FIG. 1 is not necessary, and the friction member is pressed directly against the braking member 1 during braking. Since the friction brake which makes 1 stand still is employ
  • the braking force acts from two surfaces, and the braking efficiency can be remarkably improved.
  • the magnet cover 120 in the conventional reduction gear shown in FIG. 1 is not necessary, the braking efficiency can be further improved if the distance between the disk portions 1a and 1b of the braking member 1 and the permanent magnet 5 is reduced. Is possible.
  • FIG. 3A is a schematic view showing the overall configuration of the synchronous rotation speed reduction device according to the second embodiment of the present invention, and shows a side view partly in section.
  • 3B is a cross-sectional view taken along the line IIIB-IIIB in FIG. 3A
  • FIG. 3C is a cross-sectional view taken along the line IIIC-IIIC in FIG. 3B.
  • FIG. 3D is a figure which shows schematic structure of the modification of the synchronous-rotation type
  • the second embodiment shown in FIGS. 3A to 3C is based on the configuration of the reduction gear of the first embodiment, and is different from the first embodiment in the following points.
  • the magnet holding member 4 has a surface orthogonal to the axial direction of the rotating shaft 11 and is configured to hold a plurality of permanent magnets 5 at equal intervals in the circumferential direction of the magnet holding member 4.
  • the permanent magnet 5 is arranged such that the direction of the magnetic poles (N pole, S pole) faces the axial direction of the rotating shaft 11, that is, the axial direction of the magnet holding member 4.
  • the plurality of permanent magnets 5 are arranged at equal intervals in the circumferential direction on the surface facing the inner surface of the disk portion 1a of the magnet holding member 4, and different magnetic poles are alternately arranged (FIGS. 3B and 3C). reference).
  • the magnet holding member 4 is not formed with a window as in the first embodiment, and the permanent magnet 5 is arranged on one surface.
  • a ferromagnetic material such as carbon steel, ferritic stainless steel, or cast iron at the portion of the magnet holding member 4 where the permanent magnet 5 is fixed.
  • the connected portion may be a ferromagnetic material or a nonmagnetic material such as aluminum.
  • the material of the braking member 1, particularly the disc portion 1a is a conductive material. Since others are the same as that of 1st Embodiment, the same code
  • the speed reduction device also has the same operational effects as the first embodiment.
  • the permanent magnet 5 is arrange
  • FIG. 3D is a diagram showing a modification of the second embodiment, in which permanent magnets 5 are arranged on both surfaces of the magnet holding member 4 in which no window is formed.
  • a ferromagnetic material such as carbon steel, ferritic stainless steel, cast iron or the like for the portion to which the permanent magnet 5 is fixed, but it is connected to the rotating shaft 11.
  • the portion may be a ferromagnetic material or a nonmagnetic material such as aluminum.
  • the independent permanent magnets 5 are arranged on both side surfaces of the magnet holding member 4, the degree of freedom in arrangement on both sides of the magnet holding member 4 is improved. Moreover, since the permanent magnet 5 generates an eddy current in the pair of disk portions 1a and 1b on both side surfaces of the magnet holding member 4, a large braking force can be generated.
  • FIG. 4 is a schematic view showing the overall configuration of a synchronous rotation type reduction gear system according to a third embodiment of the present invention, and shows a side view partially showing a cross section.
  • the speed reduction device of the third embodiment shown in FIG. 4 is based on the configuration of the speed reduction device of the first embodiment, and differs from the first embodiment in the following points.
  • the reduction gear of the third embodiment corresponds to a drum type, and the cylindrical portion 1c of the braking member 1 is formed longer in the axial direction than in the case of the first embodiment.
  • the magnet holding member 4 has a magnet holding ring 4a formed concentrically with the cylindrical portion 1c of the braking member 1 on the outer periphery, and a plurality of permanent magnets 5 are arranged in the circumferential direction on the outer peripheral surface of the magnet holding ring 4a. ing.
  • the permanent magnet 5 is arranged such that the direction of the magnetic pole (N pole, S pole) is arranged in the radial direction of the magnet holding member 4, and faces the inner peripheral surface of the cylindrical portion 1 c of the braking member 1. Alternatingly arranged in the circumferential direction.
  • the material of the magnet holding ring 4a is a ferromagnetic material or a weak magnetic material like the magnet holding member 4.
  • the surface layer portion of the inner peripheral surface (eddy current generating portion) facing the permanent magnet 5 is made of a highly conductive material such as copper or copper alloy. Is more preferable.
  • the rotating shaft 11 and the magnet holding member 4 rotate together, and the braking member 1 includes the cylindrical portion 1c and the magnet holding member 4 ( Due to the magnetic attraction action with the permanent magnet 5 held by the magnet holding ring 4a), it rotates in synchronization with the magnet holding member 4. For this reason, since a relative rotational speed difference does not arise between the cylindrical part 1c (braking member 1) and the permanent magnet 5 of the magnet holding ring 4a, no braking force is generated.
  • the magnet holding member 4 is rotating, so that the cylindrical portion 1c (braking member 1) and the permanent magnet 5 arranged on the magnet holding member 4 are used. There is a relative rotational speed difference between Therefore, an eddy current is generated on the inner peripheral surface of the cylindrical portion 1c. Then, due to the interaction between the eddy current generated on the inner peripheral surface of the cylindrical portion 1 c of the braking member 1 and the magnetic flux density from the permanent magnet 5, a braking force in the direction opposite to the rotational direction is generated in the rotating magnet holding member 4. The rotation of the rotating shaft 11 can be decelerated via the magnet holding member 4.
  • the speed reduction device of the third embodiment has the same effect as that of the first embodiment.
  • produces in the internal peripheral surface of the cylindrical part 1c away from the rotation center among the disk parts 1a and 1b which comprise the braking member 1, and the cylindrical part 1c. Therefore, a large braking torque is provided, and the braking efficiency can be remarkably improved.
  • the magnet cover 120 in the conventional reduction gear shown in FIG. 1 is unnecessary. Therefore, if the interval between the cylindrical portion 1c of the braking member 1 and the permanent magnet 5 is narrowed, the braking efficiency can be further improved.
  • FIG. 5A to FIG. 5C are schematic views showing the overall configuration of a synchronous rotation type reduction device according to a fourth embodiment of the present invention.
  • FIG. 5A is a side view partially showing a cross section
  • FIG. FIG. 5A is a developed view of the VB-VB cross section of FIG. 5A
  • FIG. 5C is a development view of the VC-VC cross section of FIG. 5A.
  • the speed reduction device of the fourth embodiment shown in FIGS. 5A to 5C is an example in which the configuration of the speed reduction device of the first to third embodiments is modified.
  • the cylindrical portion 1c of the braking member 1 is formed longer in the axial direction than in the first embodiment.
  • the magnet holding member 4 has a magnet holding ring 4a made of a nonmagnetic material having a smaller diameter than that of the third embodiment, and a plurality of permanent magnets are provided on the outer peripheral surface of the magnet holding ring 4a along the circumferential direction. 5 is arranged. Further, a ferromagnetic material 4b made of a magnetic material is interposed between the permanent magnets 5 adjacent to each other. Each of the plurality of ferromagnetic materials 4b is opposed to the inner surfaces of the pair of disk portions 1a and 1b in the braking member 1 and the inner peripheral surface of the cylindrical portion 1c.
  • the direction of the magnetic poles (N pole, S pole) of the permanent magnet 5 is the thickness direction of the permanent magnet 5, and different magnetic poles are alternately arranged in the circumferential direction of the magnet holding member 4 (FIGS. 5B and 5C). reference). Further, since the ferromagnetic material 4b is made of a magnetic material, the magnet holding ring 4a is made of a non-magnetic material, so that the space between them is magnetically cut off.
  • the ferromagnetic material 4b is arrange
  • the flow of magnetic flux between the permanent magnet 5 and each of the pair of disk portions 1a and 1b is indicated by dotted arrows.
  • the magnet holding member 4 rotates integrally with the rotating shaft 11, and the disk portions 1a, 1b and the cylindrical portion 1c constituting the braking member 1 are
  • the permanent magnet 5 held by the magnet holding member 4 (magnet holding ring 4a) rotates in synchronization with the magnet holding member 4 by the magnetic attraction action. For this reason, since a relative rotational speed difference does not arise between the braking member 1 and the permanent magnet 5 disposed on the magnet holding ring 4a, no braking force is generated.
  • the magnet holding member 4 is rotating, so that the disk portions 1a and 1b and the cylindrical portion 1c (braking member 1) and the magnet holding member 4 are rotated.
  • a relative rotational speed difference is generated between the permanent magnet 5 and the permanent magnet 5. Therefore, eddy currents are generated on the inner surfaces of the disk portions 1a and 1b and the inner peripheral surface of the cylindrical portion 1c.
  • the rotating magnet holding member 4 is rotated by the interaction between the eddy currents generated on the inner surfaces of the disc portions 1a and 1b of the braking member 1 and the inner peripheral surface of the cylindrical portion 1c and the magnetic flux density from the permanent magnet 5.
  • a braking force opposite to the direction is generated, and the rotation of the rotating shaft 11 can be decelerated via the magnet holding member 4.
  • the reduction gear of the fourth embodiment also has the same effect as that of the first embodiment.
  • the fourth embodiment eddy currents are generated on the inner surfaces of the disc portions 1a and 1b of the braking member 1 and the inner peripheral surface of the cylindrical portion 1c. Therefore, the braking force acts from the three surfaces of the inner surfaces of the disk portions 1a and 1b and the cylindrical portion 1c, and the braking efficiency can be further improved.
  • the magnet cover 120 in the conventional reduction gear shown in FIG. 1 is unnecessary. Therefore, if the intervals between the disk portions 1a and 1b and the cylindrical portion 1c of the braking member 1 and the permanent magnet 5 are reduced, the braking efficiency can be further improved.
  • FIGS. 6A and 6B are schematic views showing the overall configuration of a synchronous rotation speed reduction device according to a fifth embodiment of the present invention.
  • FIG. 6A is a side view partially showing a cross section
  • FIG. It is a figure which shows the VIB-VIB cross section of FIG. 6A.
  • the speed reduction device of the fifth embodiment shown in FIGS. 6A and 6B is a modification of the configuration of the speed reduction device of the first embodiment.
  • the braking member 1 has heat energy generated by the kinetic energy of the rotating shaft 11 converted by the eddy current generated in the braking member 1 and heat generated by sliding the braking member 1 with the friction member of the friction brake. Heat is also generated by energy.
  • a magnet holding member 4 holding a permanent magnet 5 is accommodated in the braking member 1. Therefore, the heat generated in the braking member 1 is accumulated in the braking member 1 and the braking member 1 becomes high temperature.
  • the temperature of the permanent magnet 5 may increase due to the radiant heat from the braking member 1, and the magnetic force held may decrease. Further, the braking member 1 itself may be permanently deformed by being overheated exceeding the allowable upper limit temperature, or may be affected by repeated overheating.
  • the heat generated in the braking member 1 is radiated by the radiation fins 2.
  • the cooling function by the radiating fins 2 is less likely to be exhibited as compared to non-braking when the braking member 1 rotates in synchronization with the magnet holding member 4. Therefore, it is desirable to devise measures to suppress the temperature rise of the braking member 1.
  • the speed reducer of the fifth embodiment includes impellers 20 a and 20 b adjacent to the outer surfaces of the pair of disk portions 1 a and 1 b constituting the braking member 1. .
  • Each impeller 20a, 20b is press-fitted and fixed to a connecting shaft 12 integral with the rotating shaft 11.
  • the speed reducer of the fifth embodiment having such a configuration, even if the rotational speed of the rotary shaft 11 decreases during braking, the impellers 20a and 20b rotate when the rotary shaft 11 is rotating. Therefore, it becomes possible to blow air from the impellers 20a and 20b toward the braking member 1 in a stationary state (see solid line arrows in FIG. 6A). Thereby, the braking member 1 can be forcibly cooled, and the temperature rise of the braking member 1 can be suppressed.
  • Such impellers 20a and 20b can be applied not only to the speed reduction device of the first embodiment but also to the speed reduction devices of the second to fourth embodiments.
  • FIG. 7 is a schematic diagram showing an overall configuration of a synchronous rotation speed reduction device according to a sixth embodiment of the present invention.
  • FIG. 7 shows a side view partly in section.
  • the speed reduction device of the sixth embodiment shown in FIG. 7 is a modification of the configuration of the speed reduction device of the first embodiment, paying attention to the suppression of the temperature rise of the braking member 1. .
  • the reduction gear device of the sixth embodiment includes a temperature sensor 21 with a sheath.
  • the temperature sensor 21 is fixed to a temperature sensor holder 22 that moves in conjunction with one of the pair of brake pads 8a and 8b, for example, the rear brake pad 8b, before and after being a friction member of a friction brake.
  • the temperature sensor 21 is connected to the temperature sensor holder 22, and the distal end of the sheath of the temperature sensor 21 is interlocked with the rear brake pad 8b moving toward the rear disc portion 1b during braking. Abuts against the outer surface of the disc portion 1b.
  • the temperature sensor 21 is connected to an actuator controller 23 that controls the driving of the actuator 9 of the friction brake.
  • the actuator controller 23 monitors the temperature of the disc portion 1b detected by the temperature sensor 21, and releases the driving of the actuator 9 when the temperature exceeds a predetermined temperature.
  • the brake pads 8a and 8b and the temperature sensor 21 are separated from the disc portion 1b and switched to the non-braking state.
  • the braking member 1 rotates together with the rotating shaft 11, and the braking member 1 is cooled by the radiation fins 2.
  • the actuator controller 23 drives the actuator 9 again to brake the braking member 1 when a predetermined time has elapsed after releasing the driving of the actuator 9.
  • the temperature rise of the braking member 1 can be suppressed.
  • the predetermined temperature when releasing the driving of the actuator 9 and the predetermined time when restarting the driving of the actuator 9 are appropriately set according to the materials and shape dimensions of the braking member 1, the magnet holding member 4 and the permanent magnet 5,
  • the actuator controller 23 is set in advance.
  • the predetermined temperature is about 300 to 400 ° C.
  • the predetermined time is about 5 to 10 seconds.
  • thermosensor 21 may be configured to move integrally with the front brake pad 8a. Further, the present invention can be applied not only to the reduction gear of the first embodiment but also to the reduction gears of the second to fifth embodiments.
  • FIG. 8 is a schematic diagram showing the overall configuration of a synchronous rotation speed reduction device according to a seventh embodiment of the present invention.
  • FIG. 8 is a side view partially showing a cross section.
  • the speed reducer of the seventh embodiment shown in FIG. 8 is a modification of the configuration of the speed reducer of the first embodiment, paying attention to the suppression of the temperature rise of the braking member 1. .
  • the reduction gear device of the seventh embodiment includes a water-cooled body (cooling member) 24.
  • the water-cooled body 24 is connected to a water-cooled body holder 25 that moves integrally with one of the pair of brake pads 8a and 8b, for example, the rear brake pad 8b, before and after being a friction member of a friction brake.
  • the water-cooled body 24 abuts against the outer surface of the disc portion 1b in conjunction with the rear brake pad 8b moving toward the rear disc portion 1b of the braking member 1 during braking.
  • a water passage 26 is formed inside the water-cooled body 24. Pipings (not shown) are connected to the entrance and exit of the water passage 26, and these pipes are connected to a cooling water system (for example, a radiator) of the vehicle. The cooling water circulates through the internal water passage 26 so that the temperature is always low.
  • the water-cooled body 24 is in contact with the rear disc portion 1b (braking member 1) during braking. Therefore, the disk portion 1 b is forcibly cooled by heat exchange with the water-cooled body 24. Thus, the temperature rise of the braking member 1 can be suppressed.
  • such a water-cooled body 24 may be configured to move integrally with the front brake pad 8a. Further, the present invention can be applied not only to the reduction gear of the first embodiment but also to the reduction gears of the second to sixth embodiments. In place of the water-cooled body 24, a cooling member through which cooling oil or the like circulates may be used.
  • FIG. 9 is a schematic diagram showing an overall configuration of a synchronous rotation speed reduction device according to an eighth embodiment of the present invention.
  • FIG. 9 shows a side view partly in section.
  • the reduction gear of the eighth embodiment shown in FIG. 9 is a modification of the configuration of the reduction gear of the first embodiment.
  • the speed reducer is based on the basic principle of converting the kinetic energy of the rotating shaft 11 into thermal energy in order to obtain a braking force, but with an electric power regeneration function that converts a part of the kinetic energy into electrical energy and recovers it. If so, energy efficiency can be improved and applications are expected to expand.
  • a vehicle equipped with a reduction gear is equipped with a number of electrical devices that require electric power, and in recent years, hybrid electric vehicles and electric vehicles that supply part or all of the propulsion power with an electric motor have attracted attention. Because it is.
  • the reduction gear of the eighth embodiment focuses on that point. That is, as shown in FIG. 9, the reduction gear according to the eighth embodiment includes the following configuration in order to also exhibit the power regeneration function.
  • the rear disc portion 1b of the pair of disc portions 1a and 1b constituting the braking member 1 has a plurality of winding coils 27 embedded in the circumferential direction on the inner surface facing the permanent magnet 5. Yes. Specifically, the inner surface of the disk portion 1b divides a region facing the permanent magnet 5 into a plurality of regions in the circumferential direction, and the winding coil 27 is formed along a groove that forms the contour of each divided region. Stored.
  • the winding coil 27 is formed by winding a conductive wire such as a copper wire a plurality of times.
  • the conductive wire 28 of the winding coil 27 is drawn out and exposed from the outer surface side of the rear disk portion 1b, and is connected to a terminal 29 installed on the outer surface of the disk portion 1b.
  • the winding coil 27 and the terminal 29 rotate together with the disc portion 1 b (braking member 1) together with the rotating shaft 11.
  • An electrical contact 30 such as a brush is slidably in contact with the terminal 29, and this electrical contact 30 is fixed to a non-rotating portion of the vehicle and connected to a storage battery mounted on the vehicle through a control circuit.
  • the braking member 1 rotates in synchronization with the magnet holding member 4 as the magnet holding member 4 rotates integrally with the rotating shaft 11. .
  • the disk portions 1 a and 1 b braking member 1
  • the permanent magnet 5 in the magnet holding member 4. Therefore, the magnetic field that acts on the inner surface of the front disc portion 1a from the permanent magnet 5 and the magnetic field that acts on the inner surface of the rear disc portion 1b and the winding coil 27 from the permanent magnet 5 do not vary. Accordingly, during non-braking, no eddy current is generated on the inner surfaces (eddy current generating portions) of the disk portions 1a and 1b, and no induced electromotive force is generated in the winding coil 27. Does not occur.
  • the magnet holding member 4 is rotated, so that it is disposed on the disk portions 1a and 1b (braking member 1) and the magnet holding member 4.
  • the magnetic field from the permanent magnet 5 acting on the inner surface of the front disc portion 1a and the magnetic field from the permanent magnet 5 acting on the inner surface of the rear disc portion 1b and the winding coil 27 both vary.
  • the magnetic field from the permanent magnet 5 fluctuates, and eddy current is generated on the inner surface.
  • the magnetic field from the permanent magnet 5 fluctuates, and an eddy current is generated on the inner surface thereof, and an induced electromotive force due to electromagnetic induction is generated in the winding coil 27.
  • a state in which the magnetic field (magnetic flux) from the permanent magnet 5 passes through the winding coil 27 and a state in which it does not pass through appear alternately. It occurs repeatedly alternately.
  • a braking force in the direction opposite to the rotation direction is generated in the magnet holding member 4 due to the interaction between the eddy currents generated on the inner surfaces of the disk portions 1a and 1b of the braking member 1 and the magnetic flux density from the permanent magnet 5.
  • the rotation of the rotating shaft 11 can be decelerated via the magnet holding member 4.
  • the induced electromotive force generated in the winding coil 27 can be recovered through the conductive wire 28, the terminal 29, and the electrical contact 30 from the winding coil 27 and stored in the storage battery as electric power.
  • the winding coil 27 may be embedded in the front disk portion 1a or may be embedded in each of the disk portions 1a and 1b. Further, the present invention can be applied not only to the reduction gear of the first embodiment but also to the reduction gears of the second to seventh embodiments. In particular, when applied to the reduction gears of the third and fourth embodiments, the winding coil 27 may be embedded in the inner peripheral surface of the cylindrical portion 1c.
  • the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.
  • the description has been given of the case where the brake members 1 are formed as conductive members by forming the disk portions 1a and 1b and the cylindrical portion 1c constituting the brake member 1 with a conductive material.
  • an eddy current generator made of a conductive material may be provided on the inner surfaces of the disk portions 1a and 1b and the inner peripheral surface of the cylindrical portion 1c.
  • you may set arbitrarily the combination of which position an eddy current generation part is formed among the inner surface of the disk parts 1a and 1b and the inner peripheral surface of the cylindrical part 1c.
  • the braking member 1 was provided with disc part 1a, 1b, and the cylindrical part 1c, and demonstrated the case where the magnet holding member 4 was enclosed from the outside, for example, the part of a connection part or a circle
  • braking member In order to reduce wear on the outer peripheral part of the outer surface of the disc part (braking member) against which the friction member is pressed during braking, heat treatment or surface treatment is applied to increase the surface hardness, or the steel sheet has excellent wear resistance. You may paste. If the braking member is an aluminum alloy, an anodized film may be provided on the surface for the purpose of improving wear resistance.
  • the impellers 20a and 20b connected to the rotating shaft 11, the actuator 9 for moving the pair of brake pads 8a and 8b toward the disk parts 1a and 1b, and the disk parts 1a and 1b have exceeded a predetermined temperature.
  • whether or not to provide an actuator controller (not shown) for releasing the driving of the actuator 9 and a cooling member (for example, a water-cooled body 24) that contacts the outer surface of the disk portions 1a and 1b can be arbitrarily set.
  • the friction brake that stops the braking member during braking is not limited to the one in which an electric linear actuator is used as a drive source and the brake pad is pressed against the outer surface of the braking member (disc portion), but an electromagnetic clutch using an electromagnet.
  • the clutch plate may be used as a friction member that presses against the outer surface of the braking member, or the drum brake mechanism may be used to press the brake shoe as a friction member against the outer peripheral surface of the braking member (cylindrical portion). There may be.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Transportation (AREA)
  • Dynamo-Electric Clutches, Dynamo-Electric Brakes (AREA)
  • Braking Arrangements (AREA)
PCT/JP2013/071799 2012-08-13 2013-08-12 渦電流式減速装置 WO2014027640A1 (ja)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US14/408,671 US9933032B2 (en) 2012-08-13 2013-08-12 Eddy-current retarding device
KR1020157000955A KR101671127B1 (ko) 2012-08-13 2013-08-12 와전류식 감속 장치
IN412DEN2015 IN2015DN00412A (ko) 2012-08-13 2013-08-12
JP2014530551A JP5673899B2 (ja) 2012-08-13 2013-08-12 渦電流式減速装置
CN201380038230.0A CN104488177B (zh) 2012-08-13 2013-08-12 涡电流式减速装置
EP13879586.9A EP2884640B1 (en) 2012-08-13 2013-08-12 Eddy-current deceleration device

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JP2012179138 2012-08-13
JP2012-179138 2012-08-13

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EP (1) EP2884640B1 (ko)
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KR101671127B1 (ko) 2016-10-31
CN104488177A (zh) 2015-04-01
US9933032B2 (en) 2018-04-03
IN2015DN00412A (ko) 2015-06-19
US20150300432A1 (en) 2015-10-22
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EP2884640A4 (en) 2016-04-13

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